US5330389A - Roller and track configuration for a tripod joint - Google Patents

Roller and track configuration for a tripod joint Download PDF

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Publication number
US5330389A
US5330389A US07/786,702 US78670291A US5330389A US 5330389 A US5330389 A US 5330389A US 78670291 A US78670291 A US 78670291A US 5330389 A US5330389 A US 5330389A
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US
United States
Prior art keywords
contact point
roller
contact
rolling
tripod
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US07/786,702
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English (en)
Inventor
Dieter Jost
Werner Krude
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GKN Driveline International GmbH
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GKN Automotive GmbH
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Filing date
Publication date
Application filed by GKN Automotive GmbH filed Critical GKN Automotive GmbH
Assigned to GKN AUTOMOTIVE AG ALTE LOHMARER STRASSE 59 5200 SIEGBURG, FED. REPUBLIC OF GERMANY reassignment GKN AUTOMOTIVE AG ALTE LOHMARER STRASSE 59 5200 SIEGBURG, FED. REPUBLIC OF GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: JOST, DIETER, KRUDE, WERNER
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Publication of US5330389A publication Critical patent/US5330389A/en
Assigned to GKN AUTOMOTIVE AG reassignment GKN AUTOMOTIVE AG CHANGE OF ASSIGNEE ADDRESS Assignors: GKN AUTOMOTIVE AG, ALTE LOHMARER STRASSE 59 SIEGBURG FEDERAL REPUBLIC OF GERMANY
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D2003/2026—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints with trunnion rings, i.e. with tripod joints having rollers supported by a ring on the trunnion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/904—Homokinetic coupling
    • Y10S464/905—Torque transmitted via radially extending pin

Definitions

  • the invention relates to tripod joints.
  • the joints include an outer joint part, with three circumferentially distributed longitudinal recesses each forming circumferentially opposed tracks, and an inner Joint part, with tripod arms which extend into the longitudinal recess and support rolling members movably and pivotably held on the tripod arms in rolling contact with the tracks.
  • the longitudinal recesses are provided with guiding means to hold the rolling members in the longitudinal recesses so as to be axis-parallel with the inner joint part.
  • tripod joints are DE 39 36 601, DE 28 31 044 or DE 37 16 962 C 2.
  • these designs solve the problem of a free rolling movement of the rolling members in the tracks under rotation and articulation conditions, the shape of the rolling members during the radially inwardly directed movement of the arms may cause the rolling members to jam between the shoulders at the longitudinal recesses which prevent the rolling members from rolling freely.
  • Attempts have been made to provide intermediate members not participating in the rolling movement.
  • An example of intermediate members are collars arranged at the roller carrier, which collars accommodate the radial forces, thereby preventing the rollers from jamming.
  • the roller assembly needs to consist of a plurality of parts and becomes expensive. Functional advantages are achieved at considerable additional costs.
  • this measure ensures that the first contact point for torque transmission is substantially constant from the point of view of position and direction.
  • the transmission forces do not influence the radial guiding forces for the rollers, which are accommodated in a second contact point.
  • a tangential plane on the surfaces of the first contact point extends either parallel to the arm axis or it opens outwardly at an angle relative to the arm axis, with an outwardly directed reaction force acting at the first contact point on the roller becoming effective in the latter case.
  • the constancy of the position of the contact point is ensured by large curved surfaces of the track and/or the rolling member.
  • the large-area curvature of the surface includes an infinite radius of curvature.
  • the rolling member In the region of the first contact point the rolling member may be cylindrical or spherical and the track surface may be planar, with the counter-face in the cross-section through the joint comprising a curvature with a large radius. It is also possible for both surfaces in the cross-section through the joint to be curved. However, it is preferable, in each case, to select radii of curvature which are clearly greater than the greatest rolling radius of the rolling member itself.
  • the second contact point accommodating the guiding forces is positioned radially inside the first contact point, with the tangential plane on the surface in this contact point in the region of the guiding shoulders inclined by approximately 45° relative to the arm axis.
  • a third contact point symmetrical relative to the first contact point may be provided radially outside, at a further guiding shoulder of the track. It is proposed that the roller should be able to move with radial play between the first and third contact points. The functioning of the third contact point may also be ensured by simple contact of the rolling member or parts related thereto with the base of the longitudinal recess itself.
  • the subject of the invention is generally applicable to joints in which the head of the arm element slides pivotably and radially movably in an internally cylindrical roller and bearing carrier; to joints with a two-part roller and bearing carrier comprising inner and outer rings pivotable relative to each other, the inner ring being radially movable on a cylindrical arm; and to joints which the internally cylindrical face of the rolling member slides on an externally spherical face of an inner ring so as to be pivotable and radially movable, the inner ring being rotatably supported on a cylindrical arm.
  • FIG. 1 is an axial end view of a tripod joint in accordance with the invention.
  • FIG. 2 is a longitudinal view partially in section of a tripod joint of FIG. 1.
  • FIG. 3 is a longitudinal section view of a second embodiment of a tripod joint in accordance with the invention.
  • FIG. 4 is a partial longitudinal section view of a third embodiment of a tripod joint in accordance with the invention.
  • FIG. 5 is a sectional view of a roller assembly in accordance with the invention as illustrated in FIGS. 1 and 2.
  • FIG. 6 is a sectional view like FIG. 5 of a second embodiment of a roller assembly in accordance with the invention.
  • FIG. 7 is a sectional view like FIG. 5 of a third embodiment of a roller assembly in accordance with the invention.
  • FIG. 8 is a cross-section view of a roller in a longitudinal recess.
  • FIG. 9 is a partial section view of a second embodiment of a roller in a recess in accordance with the invention.
  • FIG. 10 is a partial section view of a third embodiment of a roller in a recess in accordance with the invention.
  • FIG. 11 is a partial section view of a fourth embodiment of a roller in a recess in accordance with the invention.
  • FIG. 12 is a partial section view of a fifth embodiment of a roller in a recess in accordance with the invention.
  • FIG. 13 is a partial section view of a sixth embodiment of a roller in a recess in accordance with the invention.
  • FIG. 14 is a partial section view of a seventh embodiment of a roller in a recess in accordance with the invention.
  • FIG. 1 illustrates a tripod joint with an outer joint part 1 having three circumferentially distributed longitudinal recesses 2.
  • the longitudinal recesses 2 radiate from a central inner recess 3 and each form circumferentially opposed tracks 4 and 5 which will be described in more detail later.
  • the outer joint part also includes bolt holes 6.
  • the inner joint part 7 includes a central parts and arms 9 extending therefrom. Rolling members 10 are held on the arms 9 by assemblies.
  • the central part 8 includes an inner aperture 11 with inner teeth 12 to receive a driveshaft.
  • FIG. 2 shows a complete version of the joint according to FIG. 1, corresponding details having been given the same reference numbers.
  • the longitudinal section shows only one of the roller assemblies 10.
  • a shaft journal 25 is inserted into the central part 8 of the inner joint part 7.
  • a convoluted boot 26 is secured to the shaft by a first tensioning strip 27 and to the outer joint part by a second tensioning strip 28.
  • the boot seals the outer joint part 1 relative to the said shaft journal.
  • the opposite end of the outer joint part is closed by a cover30 inserted into a circumferential groove 29.
  • FIG. 3 illustrates a Joint whose roller assembly is different from that shown in FIG. 1.
  • FIG. 3 illustrates the outer joint part 41 with a sectionthrough one of the three longitudinal recesses 42 and a plan view of one ofthe tracks 45, as well as the inner joint part 47 with a central part 48 and an arm 49.
  • the arm 49 indirectly holds a rolling member 50.
  • the arm 49 is designed to be cylindrical with an internally cylindrical and externally spherical annular sleeve 51 radially sliding thereon.
  • the sleeve 51 engages an internally spherical face of an outer ring or bearing carrier 52.
  • the bearing carrier 52 holds needle bearings 53, which the outer roller 50 rolls directly thereon.
  • a shaft journal 54 is inserted into the central part 48 of the inner joint part 47. Both parts engage each other via splines 55.
  • a securing ring 56 is used for axial fixing purposes.
  • the outer joint part 41 is integrally connected to the shaft journal 57 which is also provided with sp
  • FIG. 4 shows a portion of a joint with a modified roller assembly design.
  • the outer Joint part 61 is illustrated without base and subsequent arms and with the inner recess 74 with the splines 75 not containing a shaft journal. Otherwise, the joint interior 63 and one of the longitudinal recesses 62 with one of the tracks. 65 are identifiable.
  • the inner joint part 67 with the central part 68 is again shown in section with a cylindrical arm 69 which directly carries a needle bearing 73, with an internally cylindrical, externally spherical roller 71 running thereon.
  • the roller 71 is pivotably and radially movably guided in a rolling member70.
  • FIGS. 5 to 7 each show a cross-section of part of an outer joint part 1 with a longitudinal recess 2 which passes into the inner recess 3.
  • the longitudinal recess forms tracks 4 and 5 whose shape has yet to be described in greater detail.
  • the rolling members 10 run orroll in the tracks under torque load while contacting one of the two tracks.
  • the rolling members 10 are rotatably held on a roller carrier 14 via a rolling contact bearing 13.
  • An arm 9 at the central part 8 of the inner joint part 7 engages the roller carrier.
  • the arm 9 includes a tapered neck 15 and a part-spherical head 16 which radially movably and pivotably slides in an internally cylindrical surface 17 of the roller carrier 14.
  • the rolling contact bearing is designed as a needle bearing and the rolling member 10 is held by simple discs 20 and 21 and securing rings22 and 23 secured in the roller carrier 14.
  • the roller carrier 14 is extended radially outwardly so that, optionally, depending on the radial play relative to the outer joint part, it may also assume the function of the third contact point B. That is, it may support the rolling member radially outwardly.
  • the rolling member 10 and the rolling contact bearing 13 are designed as a needle bearing held on the rolling member 14' by a cage element 24.
  • the cage element 24 assumes the function of holding and guiding the bearing needles.
  • FIG. 7 shows the rolling member 10 being held relative to the roller carrier 14" by a cage element 24 as shown in FIG. 6.
  • the roller carrier 14" is radially shortened so that, optionally, depending on the radial play relative to the outer joint part, it may assume the function of the third contact point B. That is, it may support the rolling member radially outwardly by the cage element 24.
  • FIGS. 8 to 14 each show a section or a half section view through part of the outer joint part 1, a longitudinal recess 2 and a rolling member 10. It can be seen that there are differences between the cross-sectional shapes of the rollers and tracks. The design of the roller retention assembly is insignificant. The roller 10 could be held on the inner joint part in the same way as the roller 50 is held in FIG. 3 or the roller 70 in FIG. 4.
  • FIG. 8 illustrates symbolically that under torque load, the main transmission force F R , between the rolling member 10 and the track 5,occurs in one single contact point C positioned approximately in the central roller plane E.
  • a lower guiding forceF F is transmitted independently of torque and thus independently of the force F R at a lower shoulder 19 in the track 5.
  • the force F R is exerted at an angle of approximately 45° relative to the force F F .
  • the force F F results from the movement of the respective arm in the roller and from the radial force caused by the arm movement and changes as a function of its angular position.
  • the third contact point B at the shoulder 18 there may occur a guiding force symmetrical thereto with reference to the central roller plane E.
  • the movement of the arm relative to the roller andthe track shapes described below in greater detail change the position of the first contact point C only slightly.
  • the rolling radius of the roller 10 referred to in the following Figures is given the reference symbol R.
  • the cross-section of the track 5 is designed to be convex.
  • the track 5 includes a cylindrical surface whose radius of curvature R A is greater than the rolling radius R of the rolling member 10.
  • the radius of curvature R I of the rolling member 10 itself is infinite if viewedin cross-section, i.e. the roller includes a cylindrical track shape in theregion of the first contact point C.
  • the tangential plane T at first contact point C is positioned perpendicularly to the central roller plane E.
  • FIG. 9 correspond to those of FIG. 8.
  • the radius of curvature R A of the track 5 in the region ofthe first contact point C is infinite if viewed in cross-section.
  • the track is planar, whereas the roller 10, if viewed in cross-section, has a spherical track shape whose radius of curvature R l is larger than therolling radius R of the rolling member 10.
  • the tangential plane T in contact point C is positioned perpendicularly on the central roller plane E.
  • both the track 5, in the region of the contact point C, and the rolling member 10 are convex. Both radii of curvature, radius R A of the track and radius R I of the rolling member, are greater than the rolling radius R 1 of the rollingmember 10 shown in FIG. 8.
  • the tangential plane T at first contact point c is positioned perpendicularly on the central roller plane E.
  • the track cross-section is convex.
  • the track 5 includes a cylindrical surface whose radius of curvature R A is greater than the rolling radius R of the rolling member 10 and its center is positioned below the central roller plane E.
  • the radius of curvature R l of the rolling member 10 is also infinite, its center being positioned above the central roller plane, e.g. the roller is tapered downwardly.
  • a tangential plane T forming an angle ⁇ of approximately 3° with a reference planeE' which is positioned perpendicularly to the central roller plane E.
  • the reaction force of the track 5 acting on the roller 10 includes a radial component acting radially outwardly.
  • the radius of curvature R A of the track 5 in the region of the first contact point C is infinite if viewed in cross-section, but it is positioned below the extended central roller plane E.
  • the track is planar and inclined towards the central roller axis.
  • the roller 10 again comprises a sphere whose radius of curvature R I is larger than the rolling radius R of the rolling member and whose center is positioned above the central roller plane E. Inconsequence, there is obtained a tangential plane T forming an angle ⁇ of approximately 3° with the reference plane E' which is positioned perpendicularly to the central roller plane E.
  • thereaction force of the track 5 acting on the roller 10 includes a radial component acting radially outwardly.
  • FIG. 14 shows details regarding the position of the center of curvature M A of the radius of curvature R A of track 5 in accordance with FIG. 12 and the position of the center of curvature M I of the radius of curvature R I of the roller 10 in accordance with FIG. 13.
  • the angles ⁇ and ⁇ forming the center radii relative to the first contact point C with the plane E are necessarily of the same size. Again, both radii of curvature are greater than the rolling radius of the roller 10.
  • a tangential plane T forming an angle ⁇ of approximately 3° with a reference plane E' which is positioned perpendicularly on the central roller plane E.
  • the reaction force of the track 5 acting on the roller 10 thus includes a radial component acting radially outwardly.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Rolls And Other Rotary Bodies (AREA)
US07/786,702 1990-11-02 1991-11-01 Roller and track configuration for a tripod joint Expired - Lifetime US5330389A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4034758A DE4034758C2 (de) 1990-11-02 1990-11-02 Tripodegelenk
DE4034758 1990-11-02

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US5330389A true US5330389A (en) 1994-07-19

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Application Number Title Priority Date Filing Date
US07/786,702 Expired - Lifetime US5330389A (en) 1990-11-02 1991-11-01 Roller and track configuration for a tripod joint

Country Status (4)

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US (1) US5330389A (enrdf_load_stackoverflow)
JP (1) JPH04282028A (enrdf_load_stackoverflow)
DE (1) DE4034758C2 (enrdf_load_stackoverflow)
FR (1) FR2668804A1 (enrdf_load_stackoverflow)

Cited By (17)

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Publication number Priority date Publication date Assignee Title
US5397271A (en) * 1992-07-24 1995-03-14 Gkn Automotive Ag Articulated transmission joint of the slidable type
US5507693A (en) * 1992-07-14 1996-04-16 Lohr & Bromkamp Gmbh Constant velocity universal joint
US5571047A (en) * 1993-02-20 1996-11-05 Gkn Automotive Ag Constant velocity universal joint of the tripode type
US5591085A (en) * 1993-08-12 1997-01-07 Gkn Automotive Ag Tripod constant velocity universal joint incorporating a retention system for the roller assemblies
US5836822A (en) * 1996-02-01 1998-11-17 Honda Giken Kogyo Kabushiki Kaisha Constant velocity universal joint
US5935009A (en) * 1995-11-14 1999-08-10 Ina Walzlager Schaeffler Kg Tripod constant velocity universal joint
US5989124A (en) * 1996-02-05 1999-11-23 Ntn Corporation Tripod type constant velocity universal joint
US6264565B1 (en) * 1998-12-22 2001-07-24 Ntn Corporation Tripod type constant velocity universal joint
FR2819863A1 (fr) * 2001-01-23 2002-07-26 Gkn Glaenzer Spicer Joint de transmission homocinetique et organe de transmission mecanique pour un tel joint
US6699134B2 (en) 2001-02-21 2004-03-02 Visteon Global Technologies, Inc. Anti-shudder tripod type CV universal joint
US20040048677A1 (en) * 2002-09-11 2004-03-11 Garcia Jesus Raul Bearings slip joint
US6837794B1 (en) 1996-02-05 2005-01-04 Ntn Corporation Tripod type constant velocity universal joint
WO2005073578A1 (fr) 2003-12-29 2005-08-11 Gkn Driveline S.A. Joint de transmission homocinetique
US20090137325A1 (en) * 2003-12-22 2009-05-28 Atsushi Ando Constant velocity universal joint
WO2009156516A1 (de) * 2008-06-27 2009-12-30 Tedrive Holding B.V. Tripodegelenk für ein kraftfahrzeug sowie verfahren zu dessen herstellung
DE19902701B4 (de) * 1998-04-29 2012-08-23 Kia Heavy Industries Co. Tripoden-Doppelgelenk
US20150024855A1 (en) * 2012-07-11 2015-01-22 Jtekt Corporation Tripod constant velocity joint and method of producing the same

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GB2300894B (en) * 1995-05-19 1999-03-10 Honda Motor Co Ltd Slide type universal joint
US5707293A (en) * 1969-04-16 1998-01-13 Honda Giken Kogyo Kabushiki Kaisha Slide type universal joint
DE4130963C2 (de) * 1991-09-18 1995-07-27 Loehr & Bromkamp Gmbh Tripodegelenk
DE4429479C2 (de) * 1994-08-19 1997-02-20 Loehr & Bromkamp Gmbh Tripodegelenk mit Rollensicherung
JP3212070B2 (ja) * 1995-02-27 2001-09-25 エヌティエヌ株式会社 等速自在継手
KR19990077218A (ko) 1996-01-12 1999-10-25 히로시 오카노 삼각대 형상의 등속 조인트
JP3692663B2 (ja) * 1996-10-31 2005-09-07 日本精工株式会社 トリポード型等速ジョイント
JP3043280B2 (ja) * 1996-02-15 2000-05-22 本田技研工業株式会社 等速ジョイント
JP3690074B2 (ja) * 1997-06-27 2005-08-31 日本精工株式会社 トリポード型等速ジョイント
FR2790050B1 (fr) * 1999-02-24 2002-06-07 Gkn Glaenzer Spicer Joint de transmission homocinetique et organe de transmission mecanique pour un tel joint
JP2007205508A (ja) * 2006-02-03 2007-08-16 Honda Motor Co Ltd トリポート型等速ジョイント
DE202016007595U1 (de) 2016-12-14 2017-01-26 Gkn Driveline International Gmbh Tripodegelenk

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EP0297298A1 (en) * 1987-07-01 1989-01-04 Honda Giken Kogyo Kabushiki Kaisha Sliding universal joint
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GB2226102A (en) * 1988-12-17 1990-06-20 Spicer Hardy Ltd Constant velocity ratio universal joint of the tripod type
GB2237618A (en) * 1989-11-03 1991-05-08 Loehr & Bromkamp Gmbh Tripod universal joint
EP0441382A1 (en) * 1990-02-08 1991-08-14 Toyota Jidosha Kabushiki Kaisha Plunging type constant velocity universal joint
DE4110311A1 (de) * 1990-04-07 1991-10-17 Gkn Automotive Ag Gleichlaufdrehgelenk
US5098342A (en) * 1989-04-27 1992-03-24 Nippon Seiko Kabushiki Kaisha Tripod type constant velocity joint

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JPS6421370A (en) * 1987-07-16 1989-01-24 Nec Corp Voltage detection circuit

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US3613396A (en) * 1969-02-26 1971-10-19 Peugeot Universal joint
US4192154A (en) * 1976-10-27 1980-03-11 Hitachi Construction Machinery Co., Ltd. Constant velocity universal joint
DE2831044A1 (de) * 1978-04-05 1979-10-11 Honda Motor Co Ltd Gleichlaufdrehgelenk
US4379706A (en) * 1978-04-05 1983-04-12 Honda Giken Kogyo Kabushiki Kaisha Slidable-type constant velocity universal joint
US4484900A (en) * 1980-07-07 1984-11-27 Glaenzer Spicer Articulated transmission joint including rollers
JPS5940016A (ja) * 1982-08-31 1984-03-05 Ntn Toyo Bearing Co Ltd 等速自在継手
US4571214A (en) * 1983-08-02 1986-02-18 Glaenzer Spicer Transmission joint, in particular for a motor vehicle
DE3523838A1 (de) * 1984-07-04 1986-01-16 Nippon Seiko K.K., Tokio/Tokyo Dreibeinige kupplungsverbindung
US4589856A (en) * 1985-02-28 1986-05-20 The Zeller Corporation Tripot universal joint of the end motion type
US4747803A (en) * 1985-09-17 1988-05-31 Ntn Toyo Bearing Co., Ltd. Tripod homokinetic universal joint with cylindrical rollers and a flat roller guide
DE3716962A1 (de) * 1986-09-17 1988-04-07 Ntn Toyo Bearing Co Ltd Homokinetisches universalgelenk
DE3814605A1 (de) * 1987-04-30 1988-11-17 Honda Motor Co Ltd Widerlagervorrichtung fuer ein inneres teil in einem gleit-universalgelenk
EP0297298A1 (en) * 1987-07-01 1989-01-04 Honda Giken Kogyo Kabushiki Kaisha Sliding universal joint
WO1990006451A1 (en) * 1988-11-26 1990-06-14 Hardy Spicer Limited Constant velocity ratio universal joints
GB2226102A (en) * 1988-12-17 1990-06-20 Spicer Hardy Ltd Constant velocity ratio universal joint of the tripod type
US5098342A (en) * 1989-04-27 1992-03-24 Nippon Seiko Kabushiki Kaisha Tripod type constant velocity joint
GB2237618A (en) * 1989-11-03 1991-05-08 Loehr & Bromkamp Gmbh Tripod universal joint
EP0441382A1 (en) * 1990-02-08 1991-08-14 Toyota Jidosha Kabushiki Kaisha Plunging type constant velocity universal joint
DE4110311A1 (de) * 1990-04-07 1991-10-17 Gkn Automotive Ag Gleichlaufdrehgelenk

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5507693A (en) * 1992-07-14 1996-04-16 Lohr & Bromkamp Gmbh Constant velocity universal joint
US5397271A (en) * 1992-07-24 1995-03-14 Gkn Automotive Ag Articulated transmission joint of the slidable type
US5571047A (en) * 1993-02-20 1996-11-05 Gkn Automotive Ag Constant velocity universal joint of the tripode type
US5591085A (en) * 1993-08-12 1997-01-07 Gkn Automotive Ag Tripod constant velocity universal joint incorporating a retention system for the roller assemblies
US5935009A (en) * 1995-11-14 1999-08-10 Ina Walzlager Schaeffler Kg Tripod constant velocity universal joint
US5836822A (en) * 1996-02-01 1998-11-17 Honda Giken Kogyo Kabushiki Kaisha Constant velocity universal joint
US5989124A (en) * 1996-02-05 1999-11-23 Ntn Corporation Tripod type constant velocity universal joint
US6837794B1 (en) 1996-02-05 2005-01-04 Ntn Corporation Tripod type constant velocity universal joint
DE19902701B4 (de) * 1998-04-29 2012-08-23 Kia Heavy Industries Co. Tripoden-Doppelgelenk
US6264565B1 (en) * 1998-12-22 2001-07-24 Ntn Corporation Tripod type constant velocity universal joint
FR2819863A1 (fr) * 2001-01-23 2002-07-26 Gkn Glaenzer Spicer Joint de transmission homocinetique et organe de transmission mecanique pour un tel joint
WO2002059492A1 (fr) * 2001-01-23 2002-08-01 Gkn Automotive Gmbh Joint de transmission homocinetique et organe de transmission mecanique pour un tel joint
KR100847337B1 (ko) * 2001-01-23 2008-07-21 지케이엔 오토모티브 게엠베하 등속 조인트 및 등속 조인트용 기계식 전동 부재
US6749516B2 (en) 2001-01-23 2004-06-15 Gkn Automotive Gmbh Constant velocity joint and mechanical transmission member for same
US6699134B2 (en) 2001-02-21 2004-03-02 Visteon Global Technologies, Inc. Anti-shudder tripod type CV universal joint
US20040048677A1 (en) * 2002-09-11 2004-03-11 Garcia Jesus Raul Bearings slip joint
US20090137325A1 (en) * 2003-12-22 2009-05-28 Atsushi Ando Constant velocity universal joint
US8029372B2 (en) * 2003-12-22 2011-10-04 Toyota Jidosha Kabushiki Kaisha Constant velocity universal joint
US20070135219A1 (en) * 2003-12-29 2007-06-14 Marc Francois Constant velocity joint
WO2005073578A1 (fr) 2003-12-29 2005-08-11 Gkn Driveline S.A. Joint de transmission homocinetique
US7753799B2 (en) 2003-12-29 2010-07-13 Gkn Driveline S.A. Constant velocity joint
WO2009156516A1 (de) * 2008-06-27 2009-12-30 Tedrive Holding B.V. Tripodegelenk für ein kraftfahrzeug sowie verfahren zu dessen herstellung
US20150024855A1 (en) * 2012-07-11 2015-01-22 Jtekt Corporation Tripod constant velocity joint and method of producing the same

Also Published As

Publication number Publication date
FR2668804A1 (fr) 1992-05-07
DE4034758A1 (de) 1992-06-11
DE4034758C2 (de) 1995-01-05
JPH04282028A (ja) 1992-10-07
FR2668804B1 (enrdf_load_stackoverflow) 1995-03-31

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